DE4345570B4 - Drive for cylinder of a rotary printing machine - Google Patents

Drive for cylinder of a rotary printing machine

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Publication number
DE4345570B4
DE4345570B4 DE4345570A DE4345570A DE4345570B4 DE 4345570 B4 DE4345570 B4 DE 4345570B4 DE 4345570 A DE4345570 A DE 4345570A DE 4345570 A DE4345570 A DE 4345570A DE 4345570 B4 DE4345570 B4 DE 4345570B4
Authority
DE
Germany
Prior art keywords
cylinder
cylinders
characterized
drive
drive according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
DE4345570A
Other languages
German (de)
Inventor
Dieter Koch
Felix Schneider
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wifag Maschinenfabrik AG
Original Assignee
Wifag Maschinenfabrik
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wifag Maschinenfabrik filed Critical Wifag Maschinenfabrik
Priority to DE19934344896 priority Critical patent/DE4344896C5/en
Priority to DE4345570A priority patent/DE4345570B4/en
Application granted granted Critical
Publication of DE4345570B4 publication Critical patent/DE4345570B4/en
Anticipated expiration legal-status Critical
Application status is Expired - Fee Related legal-status Critical

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Classifications

    • BPERFORMING OPERATIONS; TRANSPORTING
    • B41PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41FPRINTING MACHINES OR PRESSES
    • B41F13/00Common details of rotary presses or machines
    • B41F13/008Mechanical features of drives, e.g. gears, clutches
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B41PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41FPRINTING MACHINES OR PRESSES
    • B41F13/00Common details of rotary presses or machines
    • B41F13/004Electric or hydraulic features of drives
    • B41F13/0045Electric driving devices
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B41PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41PINDEXING SCHEME RELATING TO PRINTING, LINING MACHINES, TYPEWRITERS, AND TO STAMPS
    • B41P2213/00Arrangements for actuating or driving printing presses; Auxiliary devices or processes
    • B41P2213/70Driving devices associated with particular installations or situations
    • B41P2213/73Driving devices for multicolour presses
    • B41P2213/734Driving devices for multicolour presses each printing unit being driven by its own electric motor, i.e. electric shaft

Abstract

Drive for cylinder of a rotary printing machine, the
a) a cylinder unit (20) having a plurality of cylinder pairs (10) each comprising a blanket cylinder (2) and a plate cylinder (3), which are mechanically coupled to each other for driving together by a pair of cylinders (10) a first motor (5), and a Central cylinder (6) forming an impression cylinder for a plurality of the blanket cylinders (2),
b) wherein the central cylinder (6) is either driven by its own further motor (6a) or mechanically coupled to its drive with one of the blanket cylinder (2), and
c) each comprising a controller (23) for the motors (5, 6a),
characterized in that
d) the first motors (5) per cylinder pair (10) each by means of a toothed belt (11) or by means of a gear coupling one of the cylinders (2, 3) of the respective cylinder pair (10) drive,
e) that in the cylinder pairs (10) of the by means of the respective first motor (5) driven cylinder (2) on the other cylinder (3) of the respective ...

Description

  • The present invention relates to a drive for cylinders of a rotary printing machine.
  • Conventional rotary printing presses are driven by a main drive via a mechanical longitudinal shaft, also called a king shaft. A disadvantage of these printing machines is the mechanical effort required to compensate for the torsion of the longitudinal shaft occurring during the run. As a result, a mechanical circumferential register adjustment of pressure points of the printing machine during the run is necessary.
  • Attempts are also made to replace the mechanical longitudinal shaft between the individual pressure units by an electric longitudinal shaft. Each printing unit receives a separate electric drive. In addition to the high mechanical complexity, which still has to be operated because of the complexity of the individual printing units with a plurality of pressure points, in this case a high control-technical effort is added since the synchronous operation of the individually driven printing units must also be ensured.
  • To avoid the problems mentioned in the DE 41 38 479 A1 proposed to drive the cylinders of the printing press by a respective electric motor.
  • From the DE 42 14 394 A1 is a Regelelleitsystem for such a printing machine with each individually driven cylinders known. The individual drives of the cylinders and their drive controller can be summarized to groups of pressure groups arbitrarily. The groups of printing groups are assigned to folders from which they obtain their position reference. Essentially, the proposed control system consists of a fast BUS system for the individual drives and the drive controllers of a print group and a higher-level control system for managing print group groups.
  • Although the concept of the individually driven cylinders pursued in these two publications allows a high versatility of use, at the same time it requires a very high number of drive motors and, like the DE 42 14 394 A1 shows a high control effort for this large number of individual drives. In addition, a variety of motors must be used. If only a few engine sizes are used, otherwise oversized motors would otherwise be used for different applications. Both drive the price of such a printing press.
  • The present invention has the object, on the other hand, to provide a highly flexible, yet economical drive a rotary printing press.
  • This object is solved by the subject matter of claim 1.
  • The subclaims are directed to convenient and not obvious obvious embodiments of the subject matter of claim 1.
  • According to the invention form blanket cylinder and plate cylinder of a rotary printing machine in pairs a cylinder group, in each of which a blanket cylinder and a plate cylinder are mechanically coupled together and are driven together by a separate drive motor per cylinder group.
  • By this group summary of the two cylinders and their equipment with a single drive for at least one pair of cylinders, the number of required drive motors is significantly reduced; at least halved compared to the single drive concepts. The mechanical coupling of these two cylinders associated with each other by printing technology, preferably a gear coupling with straight or helical gears, offers significant price advantages over the concept of the individually driven cylinders. With regard to the versatility of use, no significant losses compared to the single drive concept have to be made. Thus, both the Umfangsregister- and the Seitenregisterverstellung each blanket cylinder individually and to any other blanket cylinder, if necessary, be made coordinated. Due to the cylinder groups corresponding to the invention, each with its own drive motors optimum pressure points can be formed in a rotary printing machine in technical and economic terms. In this context, in each case the printing couples are understood to mean the pairs of cylinders between which a paper web to be printed passes and is printed on one side or on both sides. Accordingly, to a pressure point formed according to the invention each include a cylinder group and a corresponding impression cylinder, which may belong to the cylinder group, but need not. In the latter case, a pressure point is formed by two cylinder groups assigned to one another. In terms of drive technology, however, the pressure points of the printing press in both cases are mechanically independent in themselves, d. H. the pressure points of the printing press are electrically coupled together.
  • Preferably, in the cylinder groups according to the invention, the blanket cylinder is driven, which in turn drives off via the mechanical coupling onto the plate cylinder of the same cylinder group. In another However, embodiment of the invention, the drive can also drive the plate cylinder shaft, so that the blanket cylinder is driven only via the mechanical coupling of the plate cylinder. While the Anrieb on the plate cylinder advantageously requires little effort for on and off of the blanket cylinder, the blanket cylinder on the other hand is decisive for the positional accuracy or circumferential register setting. The former solution has the advantage that the cylinder, which ultimately comes into direct contact with a paper web to be printed, does not first have to be driven by a possibly affected with game transfer member.
  • A cylinder group can be extended according to the invention by an impression cylinder for the blanket cylinder. This third cylinder of the cylinder group thus formed is mechanically coupled to the blanket cylinder, preferably by a further gear coupling. Such a cylinder group already represents a pressure point, between the blanket and impression cylinders, the paper web to be printed is passed. The impression cylinder can be a steel or even another blanket cylinder for double-sided printing. Such an impression cylinder may in particular also be a central cylinder of a cylinder unit with, for example, nine or ten cylinders. In an alternative, likewise preferred embodiment of the invention, such a central cylinder is driven by its own drive motor. This type of summary provides the highest versatility for a cylinder unit. Thus, in this case, each of the central cylinder associated cylinder groups of blanket and plate cylinder individually and independently of the other cylinder groups are reversed, as is required for example for alternating pressure or for the flying plate change.
  • The output of a drive motor to the respective cylinder group is preferably carried out by means of a toothed belt. Opposite in the DE 41 38 479 A1 proposed solution of sitting on the drive shaft of the driven cylinder rotor of the electric motor such a timing belt has a high elasticity. For the control concept of driving a cylinder group, however, the possibility of high damping of the mechanical system consisting of a drive motor and the driven cylinders given by the use of a toothed belt is of great value, as will be explained later. In principle, however, the invention also allows the direct drive, which may even be advantageous for small cylinders. Compared to a gear drive between the drive motor and the driven cylinder of a cylinder group, as he may also apply, a toothed belt has the advantage of a backlash-free run and a not absolutely fixed gear ratio.
  • In contrast, gears are provided for the mechanical coupling between the cylinders within a cylinder group, although other transmission elements are quite conceivable. The meshing gears may be straight or helical teeth. When helical gears for lateral register adjustment of the blanket cylinder is moved longitudinally, while his drive and / or driven gears remain stationary according to the invention. Otherwise, the Seitenregister- also a circumferential register adjustment would be required. When sprocket wheels are used, the blanket cylinder along with its fixed gear or its gears is simply moved longitudinally.
  • The inking roller or the inking rollers of an inking unit, which is assigned to a cylinder group, can according to the invention be mechanically coupled to this cylinder group, so that the inking roller or the inking rollers are driven by the drive motor of this cylinder group. By this solution, the technical control effort can be kept low. On the other hand, the mechanical coupling of the inking unit within the meaning of the modular principle pursued by the invention is not quite as ideal as the more preferred self-propulsion for the roller or the rollers of the inking unit. Thereafter, each inking unit has its own drive motor for its ink rollers. Such a drive motor also drives preferably via a backlash-free timing belt with high damping and optionally via a reduction gear transmission, the ink roller or in the case of multiple ink rollers the plate cylinder of the corresponding cylinder group closest to the ink roller. The peripheral speed of this ink roller is advantageously adjustable, in particular with negative slip relative to the plate cylinder, so that the peripheral speed of the ink roller is slightly less than that of the corresponding plate cylinder.
  • At least the drive motors of the cylinder groups of a cylinder unit operating on the same pressure side of a paper web are advantageously position-controlled. Preferably, a so-called ideal position control, d. H. a delay-free position control with a following error connection. However, this, due to technical reasons desired, complex type of position control can certainly be dispensed with. A simple position control is likewise a preferred, in particular less expensive, embodiment of the invention.
  • The regulation of the position and / or the speed of the controlled cylinder of a cylinder group or a roller of an inking unit according to the invention by means of a controller for the drive motor by the target / actual comparison of the output signals of a setpoint generator and an actual value encoder, this Actual value encoder detects the position and / or the rotational speed of the cylinder or the roller. In contrast to the known regulations in rotary printing machines, a load transmitter is thus used for the control. In contrast, hitherto in mechanical press a mechanical encoder has been used on the motor side for detecting the engine speed or the rotor angular position of the engine for the target / actual comparison of the engine control. With this conventional control, with high mass inertia ratios of the load to the engine, the dynamic limits are quickly encountered. When the control system becomes unstable, the engine starts to oscillate while the load remains relatively quiet.
  • In control technology, differential overrides, control cascades and active filters are known for so-called dual-mass oscillators, which, however, all require a great deal of control engineering effort. For the load / motor systems described above, i. H. the self-propelled cylinder groups, it has surprisingly been found to be completely sufficient to lead the control essentially by means of an actual value, which has been determined by an on the load, namely on one of the cylinders of a cylinder group, attached actual value encoder. This actual-value angular position and / or speed of the cylinder in question - enough to achieve a high level of dynamics and control quality even alone.
  • By the actual value to be controlled according to the invention is taken off the load, what is measured, what exactly has to run, namely the load, not the motor, is also measured. The existing of the drive motor, a coupling and the load mechanical replacement system is to be regarded as a low-pass filter. In this type of control, the low-pass filter of the motor-coupling-load-distance system is used to filter shocks and vibrations that occur in the controlled system. Such shocks and vibrations are thus returned to a reduced extent in the controller. The danger of a Aufschaukelung is thereby reduced. The dynamics of the control and thus the control quality can be significantly increased compared to the described conventional control with identical coupling.
  • The figuratively speaking from the motor side to the load side migrated actual value encoder forms the main control variable for the controller of the engine, d. H. the motor is guided from the load side by its actual value. According to a particularly preferred embodiment of the invention, no mechanical actual value encoder for detecting the position or the rotational speed of the engine is required in the context of the control of the engine. An optionally integrated in the engine actual value detection can be used advantageously for the pure drive monitoring, possibly for a motor emergency shutdown.
  • The actual value encoder for the control is mounted according to the invention on the torque-free shaft end of the driven cylinder of a cylinder group or the driven roller of an inking unit.
  • Particularly advantageous electric asynchronous motors are used as the drive motors. So far, an asynchronous motor has only been used when a small load had to be driven by means of a large motor. For the present case, in which a drive motor drives a cylinder group or the rollers of an inking unit, in which therefore the driven load has a comparatively high mass moment of inertia relative to the drive motor, the use of asynchronous motors is not known. For the purposes of the control according to the invention with a load transmitter instead of a motor encoder asynchronous motors are particularly suitable. Asynchronous motors have a higher field stiffness than the DC motors previously used for the applications in question, so that their use improves the dynamics and control quality of the system to be controlled. However, the use of other engine types, recordable DC motors, is not excluded in principle.
  • The stability of the control is further improved by the preferred use of a backlash-free toothed belt with high damping as coupling between the engine and the load.
  • The drive motor can even be left out of consideration in the two-mass oscillator in question. The load acting as a low-pass filter is insensitive to the vibrations of the much smaller engine on the other hand. On the other hand, the effects of the load on the drive motor can be neglected.
  • The concept of pairing blanket and plate cylinders into groups of cylinders, optionally adding another impression cylinder, provides the highest level of flexibility while significantly reducing the price of such an organized press to a single-cylinder printing press. For a composite of such cylinder groups printing machine drive motors in only two, at most three power classes are required, while in direct and individually driven cylinders are basically each separate motors for cylinders of various lengths and diameters required. By means of the toothed belt drive used in accordance with the invention, the mass moment of inertia of moment between the load and the motor, which may fluctuate within wide limits, can be absorbed and matched to one another by appropriate selection of the ratio. The reduction in the number of drive motors together with the advantage that motors need to be provided only in a few performance classes, already offers significant price advantages. This advantage is reinforced by the use of the simple control according to the invention, which is also flexibly adaptable to changing inertia conditions. The advantages achieved by the invention with increasing printing machines, ie with increasing number of printing units and pressure points per machine, more and more advantage. In particular, the invention finds use in the construction of offset rotary printing presses; but it is not limited to this type of machine.
  • Preferred embodiments of the present invention will be explained below with reference to the figures. In this case, further features and advantages of the invention are disclosed. Show it:
  • 1 a pressure point with two cylinder groups;
  • 2 a pressure point with a cylinder group;
  • 3 a cylinder unit with a self-propelled central cylinder and four cylinder groups;
  • 4 a cylinder group with an associated self-propelled inking roller;
  • 5 a control of the drive for a cylinder group according to the prior art;
  • 6 a control for driving a cylinder group according to the invention;
  • 7 a comparison of the dynamic behavior of a conventional control and regulation according to the invention as a function of the mass moment of inertia ratio of motor and load;
  • 8th a comparison of the dynamic behavior of a conventional control and regulation according to the invention as a function of the torsional rigidity of the coupling between the engine and the load; and
  • 9 a control diagram of the regulator;
  • At an in 1 The printing point shown becomes a paper web to be printed 1 between the two opposite blanket cylinders 2 two cylinder groups 10 passed. The two cylinder groups 10 are each through the blanket cylinder 2 and an associated plate cylinder 3 formed, which are mechanically coupled together for the common drive. The mechanical coupling is schematically represented by a connecting line between the centers of the two cylinders 2 and 3 indicated. In the embodiment according to 1 are each the blanket cylinder 2 each cylinder group 10 by a three-phase motor 5 driven. The configuration according to the 1 , in each case only one blanket cylinder 2 and a plate cylinder 3 by a mechanical coupling to a cylinder group 10 are characterized by their simple design and the highest possible degree of freedom in configuration in the formation of pressure points or pressure point groups.
  • 2 shows a variant for forming a pressure point, in which a counter-pressure cylinder 4 for the blanket cylinder 2 with this blanket cylinder 2 is mechanically coupled. In this embodiment, the cylinder group continues 10 from the blanket cylinder 2 , its impression cylinder 4 and the plate cylinder 3 and their mechanical coupling together, so that the pressure point by a single cylinder group 10 is formed. In the embodiment of 2 is unlike the the 1 not the blanket cylinder 2 but the plate cylinder associated with this cylinder 3 by a three-phase motor 5 driven. Advantage of this variant for the combination of cylinders to a cylinder group is their constant conveying behavior because of the mechanical coupling of the blanket cylinder 2 with his impression cylinder 4 and that because of this mechanical coupling no direct mutual influence of the cylinder 2 and 4 takes place. The impression cylinder 4 may be a second blanket cylinder or a steel cylinder, for example, a central cylinder of a nine or ten-cylinder unit.
  • The assignment of the motors 5 to the blanket cylinders 2 or the plate cylinders 3 can basically be reversed in both embodiments. The drive of the plate cylinder 3 has the advantage that the cylinder group 10 easier to reverse, while in the other case when driving the blanket cylinder 2 the on the paper web 1 directly printing cylinder is driven and thereby a drive free of play-related transmission elements, such as gears, is possible.
  • In 3 is a cylinder unit 20 represented, consisting of a central steel cylinder 6 and four, this central cylinder 6 assigned cylinder groups 10 , In each case a blanket cylinder 2 and a plate cylinder 3 are in this embodiment to a cylinder group 10 summarized. For the drive of the central cylinder 6 is a separate three-phase motor 6a intended. Likewise, however, the central cylinder could 6 with one of the four cylinder groups 10 a cylinder group according to the in 2 form variant shown. This would be the own engine 6a for the central cylinder 6 be saved. On the other hand, however, offers in 3 illustrated summary of the smallest possible cylinder groups 10 and self-propelled central cylinder 6 to a cylinder unit 20 the highest possible flexibility in terms of configuration options. This derived from the basic variants described above configuration of a cylinder unit 20 has the technical advantage that the so-called fan-out effect is very limited. Each of the blanket cylinders 2 is also easy to switch to rubber / rubber production. The possibilities to switch to different types of alternating pressure are also not limited.
  • As this embodiment shows, a cylinder group formed of cylinder pairs 10 in terms of their configurability a concept with each individually driven cylinders on a par.
  • In 4 is the interaction of a blanket / plate cylinder pair 2 . 3 existing cylinder group 10 with a paint roller 7 shown. This has the ink roller 7 via its own drive by a motor 5 that's the engine 5 for the cylinder group 10 may be identical, but not necessarily. The motor 5 for the ink roller 7 drives over a toothed belt 15 and a gear pair 16 . 17 , where the gear 17 on the shaft of the ink roller 7 sits, the paint roller 7 at. The different moments of inertia of the engine 5 and the ink roller 7 By suitable choice of the gear ratios when driven through the timing belt 15 and the gear pair 16 . 17 defused.
  • The peripheral speed of the ink roller 7 is adjustable with a slight negative slip against the plate cylinder 3 , This can be counteracted the risk that by a gear pair 12 . 13 formed mechanical coupling between the blanket cylinder 2 and the plate cylinder 3 is lifted from the tooth mesh.
  • The drive of the cylinder group 10 done by the engine 5 over the timing belt 11 on the blanket cylinder 2 , The mechanical coupling between the blanket cylinder 2 and the plate cylinder 3 the same cylinder group 10 form the two gears 12 and 13 , To defuse a high ratio of the mass moments of inertia of load and drive, namely cylinder group 10 and engine 5 , the speed of the engine 5 over the timing belt 11 appropriately stocky. This timing belt 11 is the elastic coupling between the engine 5 and the driven cylinder group 10 , Compared to a basically also suitable direct coupling or a gear coupling is with the timing belt 11 a very high damping of the motor / load system 5 . 10 achieved. The same applies in principle to the drive of the ink roller 7 and its coupling member, the timing belt 15 , Furthermore, a large constructive clearance is created by the choice of a toothed belt drive because of the continuously variable transmission. The motors 5 for the cylinder group 10 or the ink roller 7 are each three-phase motors with a high field stiffness. Again, the modular principle of the formation of cylinder groups or groups of rollers with toothed belt coupling to the drive motor comes into play, since with less engine performance sizes, the entire variety of cylinder or roller lengths and diameters can be equipped with ensprechend different moments of inertia.
  • The two gears 12 and 13 showing the mechanical coupling between the blanket cylinder 2 and the plate cylinder 3 may be helical or spur gears. In the case of helical gears, the blanket cylinder 2 in the Seitenregisterverstellung longitudinally displaced while the gear 12 and the corresponding gear for the timing belt 11 remain stationary, ie these two gears are on the cylinder shaft 14 mounted longitudinally displaceable. In the case of a straight toothing of the two gears 12 and 13 sit the gear 12 and the gear for the timing belt 11 stuck on the shaft 14 and be together with the blanket cylinder 2 and the engine 5 for the cylinder group 10 moved longitudinally together.
  • In contrast to the regulations known in rotary printing machine construction, the motor / load system 5 . 10 guided by an actual value, the one of the load side, namely at the torque-free end of the shaft 14 the blanket cylinder 2 attached mechanical loader 21 is produced. The same type of regulation, namely with a load-free shaft end of the inking roller 7 attached loader 27 is used to control the speed of this ink roller 7 selected.
  • A known in printing machine construction control is in 5 shown schematically. The regulation of the engine 5 that has a flexible coupling 24 a burden 25 drives, by means of a regulator 23 , Weight 25 For example, a heavy roll or cylinder or roller or cylinder system whose mass moment of inertia is typically more than five times that of the engine 5 is. Nevertheless, the control of this motor / load system is optimized for performance and with sufficiently high control quality for the number of revolutions or the angular position and the speed of the load 25 be managed. It should be to the coupling 24 The motor and load requirements are not too high in terms of their torsional rigidity and backlash.
  • Both known systems, such as one in 5 is a mechanical actual value encoder 21 for generating a position or speed and the position of the rotor of the motor 5 characteristic electrical signal attached to this rotor. Weight 25 is with the coupling 24 , which has an elasticity and possibly a certain play, attached to the motor shaft end. The coupling and the load are outside the actual control loop. However, you can influence this by means of the acceleration torques acting on the motor shaft.
  • This system quickly reaches its dynamic limits with high mass inertia ratios from load to motor. If the control system becomes unstable, the engine will vibrate while the load remains relatively quiet.
  • 6 shows, however, a scheme in which, as in 4 already shown, the reference variable for the control of a donor 21 is generated at the load 25 and not on the engine 5 is appropriate. This actual value encoder 21 is at the free shaft end of the load, in the embodiment at the free shaft end of the blanket cylinder 2 a cylinder group 10 , appropriate. This actual value encoder 21 is therefore referred to as loader in the following. The coupling 24 is due to the already described timing belt 11 formed with respect to a direct coupling or a gear coupling high elasticity but also high damping. In addition, this coupling 24 with a toothed belt play free.
  • The needed for the control, from the loader 21 generated actual value, the angular position of the blanket cylinder 2 or whose speed and its angular position represents is on the controller 23 recycled. A computer-generated setpoint from the setpoint generator 22 is compared with this actual value and to form a control signal for the motor 5 used.
  • In this regulation are the coupling 24 and the load 25 within the actual control loop. The load and the coupling 24 Form a low-pass filter for the resulting in the control system shocks and vibrations, which thus only in a reduced degree in the controller 23 and therefore can not lead to unwanted suggestions of the regulation. As a result, the dynamics and the quality of control compared to conventional systems are significantly increased even with otherwise the same coupling. The system, consisting of governor, engine, clutch and cylinder, is already substantially more damped. Resonance peaks therefore do not occur to the same extent. The controller can therefore be set faster without leaving the stable work area.
  • One on the engine if necessary 5 attached, according to the embodiment 6 shown actual value detection can be for additional monitoring of the engine 5 , for example, at a desired emergency shutdown of the engine 5 be used.
  • In the diagrams of 7 and 8th is the dynamic behavior of the two regulations according to the 5 and 6 compared. As a measure of the dynamics of the control, the reciprocal value of the reset time T i of the drive is selected. In 7 the dynamics is shown as a function of the mass inertia ratio of load to motor with identical coupling and identical phase reserve. This shows clearly that the scheme after 6 with the actual value detection on the load, especially with larger mass inertia ratios of the actual value detection on the motor according to 5 is clearly superior.
  • In 8th is the dynamics as a function of the torsional rigidity of the coupling 24 imaged at constant mass inertia ratio and identical phase reserve. This shows the regulation 6 especially at low torsional stiffness of the coupling compared to the conventional control accordingly 5 think.
  • 9 Finally, shows the control diagram of the regulator 23 , The setpoint and the actual value, in the exemplary embodiment, the desired or actual center position of a blanket cylinder 2 , are used to form the difference setpoint actual value a first differential amplifier 31 fed. The difference D 1 formed there is a first proportional amplifier 34 fed and proportional amplified signal K 1 XD 1 to a second differential amplifier 35 given. In parallel, the setpoint and the actual value are each a differentiator 32 respectively. 33 supplied, differentiated and the corresponding output signals S. s and s. i to the second differential amplifier 35 guided. The sum formed there k 1 D 1 + S. s - S. i is in a second proportional amplifier 36 reinforced and via an integrator 37 a current regulator for the motor 5 fed.

Claims (14)

  1. Drive for cylinders of a rotary printing press, which a) a cylinder unit ( 20 ) with several pairs of cylinders ( 10 ) each from a blanket cylinder ( 2 ) and a plate cylinder ( 3 ), for common drive by per pair of cylinders ( 10 ) a first engine ( 5 ) are mechanically coupled together, and a central cylinder ( 6 ), which has an impression cylinder for several of the blanket cylinders ( 2 ), b) wherein the central cylinder ( 6 ) either from its own, additional engine ( 6a ) or mechanically driven by one of the blanket cylinders ( 2 ), and c) one controller each ( 23 ) for the engines ( 5 . 6a ), characterized in that d) the first motors ( 5 ) per cylinder pair ( 10 ) each by means of a toothed belt ( 11 ) or by means of a gear coupling one of the cylinders ( 2 . 3 ) of the respective cylinder pair ( 10 ), e) that in the cylinder pairs ( 10 ) of which by means of the respective first motor ( 5 ) driven cylinder ( 2 ) on the other cylinder ( 3 ) of the respective cylinder pair ( 10 ) and f) that the circumferential register adjustment of each blanket cylinder ( 5 ) is made individually and adapted to any other desired blanket cylinder.
  2. Drive according to claim 1, characterized in that the blanket cylinders ( 2 ) from the first engines ( 5 ) and from the blanket cylinders ( 2 ) on the plate cylinder ( 3 ) is driven off.
  3. Drive according to one of the preceding claims, characterized in that the drive from the first motors ( 5 ) on the cylinders ( 2 . 3 ) by means of toothed belt ( 11 ) he follows.
  4. Drive according to one of the preceding claims, characterized in that the mechanical coupling between the cylinders ( 2 . 3 ; 2 . 3 . 4 ) of a cylinder pair ( 10 ) by gears ( 12 . 13 ) is formed.
  5. Drive according to one of the preceding claims, characterized in that at least one inking roller ( 7 ) of an inking unit, one of the pairs of cylinders ( 10 ) is assigned mechanically with this pair of cylinders ( 10 ) is coupled.
  6. Drive according to one of claims 1 to 4, characterized in that for driving at least one ink roller ( 7 ) of an inking unit, one of the cylinder pairs ( 10 ), a separate drive motor ( 5 ) is provided.
  7. Drive according to claim 5, characterized in that a peripheral speed of a against the plate cylinder ( 3 ) one of the cylinder pairs ( 10 ) rolling roller ( 7 ) is adjustable, in particular, that a negative slip relative to the plate cylinder ( 3 ) is adjustable.
  8. Drive according to one of the preceding claims, characterized in that one controller each has a setpoint generator ( 22 ) and an actual value encoder ( 21 ; 27 ) and that the actual value encoders ( 21 ; 27 ) a position and / or a rotational speed of each cylinder ( 2 . 3 or 4 ) of the cylinder pairs ( 10 ) to capture.
  9. Drive according to claim 8, characterized in that one of the actual value encoder ( 21 ; 27 ), the main control variable for the controller ( 23 ).
  10. Drive according to claim 8 or 9, characterized in that for the regulation of the first motors ( 5 ) no mechanical actual value encoder for detecting the position or the rotational speed of the respective first motor ( 5 ) is provided.
  11. Drive according to one of claims 8 to 10, characterized in that no further mechanical actual-value encoder is provided for the control.
  12. Drive according to one of claims 8 to 11, characterized in that a mechanical encoder on the respective first motor ( 5 ) is provided whose output signal as an input signal for an emergency shutdown of the respective first engine ( 5 ) is used.
  13. Drive according to one of claims 8 to 12, characterized in that the actual value encoder ( 21 ; 27 ) on torque-free shaft ends of the first motors ( 5 ) driven cylinder ( 2 or 3 ) are mounted.
  14. Drive according to one of the preceding claims, characterized in that the first motors ( 5 ) are formed by electric asynchronous motors.
DE4345570A 1993-12-29 1993-12-29 Drive for cylinder of a rotary printing machine Expired - Fee Related DE4345570B4 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE19934344896 DE4344896C5 (en) 1993-12-29 1993-12-29 Drive for cylinder of a web-fed rotary printing machine
DE4345570A DE4345570B4 (en) 1993-12-29 1993-12-29 Drive for cylinder of a rotary printing machine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE4345570A DE4345570B4 (en) 1993-12-29 1993-12-29 Drive for cylinder of a rotary printing machine

Publications (1)

Publication Number Publication Date
DE4345570B4 true DE4345570B4 (en) 2011-06-16

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Family Applications (3)

Application Number Title Priority Date Filing Date
DE9321320U Expired - Lifetime DE9321320U1 (en) 1993-12-29 1993-12-29 Rotary printing press with pairwise combined to form groups of cylinders the blanket and plate or forme cylinders
DE4345570A Expired - Fee Related DE4345570B4 (en) 1993-12-29 1993-12-29 Drive for cylinder of a rotary printing machine
DE4405658A Expired - Fee Related DE4405658C5 (en) 1993-12-29 1994-02-22 Drive for cylinder of a web-fed rotary printing machine

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Also Published As

Publication number Publication date
DE4405658A1 (en) 1995-09-07
US6338298B2 (en) 2002-01-15
DE4405658C2 (en) 1997-08-14
DE9321320U1 (en) 1997-04-24
DE4405658C5 (en) 2007-06-28
US20010017087A1 (en) 2001-08-30

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